EP1882559A1 - Outil à main doté d'un dispositif de découplage - Google Patents

Outil à main doté d'un dispositif de découplage Download PDF

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Publication number
EP1882559A1
EP1882559A1 EP07112663A EP07112663A EP1882559A1 EP 1882559 A1 EP1882559 A1 EP 1882559A1 EP 07112663 A EP07112663 A EP 07112663A EP 07112663 A EP07112663 A EP 07112663A EP 1882559 A1 EP1882559 A1 EP 1882559A1
Authority
EP
European Patent Office
Prior art keywords
spring
bearing
bearing element
latch
loaded
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP07112663A
Other languages
German (de)
English (en)
Other versions
EP1882559B1 (fr
Inventor
Axel Fischer
Roland Meuer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hilti AG
Original Assignee
Hilti AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hilti AG filed Critical Hilti AG
Publication of EP1882559A1 publication Critical patent/EP1882559A1/fr
Application granted granted Critical
Publication of EP1882559B1 publication Critical patent/EP1882559B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/04—Handles; Handle mountings
    • B25D17/043—Handles resiliently mounted relative to the hammer housing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/006—Vibration damping means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2222/00—Materials of the tool or the workpiece
    • B25D2222/54—Plastics
    • B25D2222/57—Elastomers, e.g. rubber
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2222/00—Materials of the tool or the workpiece
    • B25D2222/54—Plastics
    • B25D2222/69—Foamed polymers, e.g. polyurethane foam
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/371—Use of springs

Definitions

  • the invention relates to a hand tool, in particular in the form of an optionally usable as a drill or chisel hammer electro combi hammer.
  • a hand tool in particular in the form of an optionally usable as a drill or chisel hammer electro combi hammer.
  • This has a housing in which a working means is provided, which is reciprocated during operation along a spaced apart from a center of gravity of the power tool working axis and which is parallel to a first direction.
  • the working fluid may be formed by a percussion piston of an electropneumatic striking mechanism.
  • the hand tool has a handle which is held on the housing via a decoupling arrangement to reduce the transmission of vibrations from the housing to the handle.
  • the decoupling arrangement comprises a first spring-loaded bearing and a second spring-loaded bearing in the form of a rotary bearing, which is spaced further apart from the working axis in a second direction transverse to the working axis than the first spring-loaded bearing.
  • torsional vibrations are generated on the housing during operation by the distance between the working axis and the center of gravity.
  • a sprung rotary bearing on which a certain rotational movement of the handle relative to the housing against a spring force is made possible, the transmission of vibrations arising from these torsional vibrations can be reduced to the handle. This achieves not only a reduction in vibration along the first direction but also a significant reduction in vibration along the second direction and thus a high level of comfort when holding the device.
  • the vibration reduction is carried out essentially on the respective largely vibration-decoupled suspension, which virtually isolates a large part of the vibrations occurring during operation of the handle, depending on the spring means used also a more or less large damping effect is present. In the following, this is referred to as decoupling, irrespective of the proportion of the damping effect.
  • a disadvantage of the known hand tool is that due to the all-round spring action on both Abfederungs Symposiumen no adequate decoupling of the handle of the torsional vibrations occurring on the housing is possible. Rather, the spring behavior of both Abfederungs Symposiume is superimposed with regard to the torsional vibrations. Due to the relatively stiff lower Abfederungs Schemees and the superposition with acting in the second direction spring action of the upper Abfederungs Symposiumes remains in operation, a relatively high vibration along the second direction.
  • the present invention has for its object to avoid the disadvantages mentioned in a generic hand tool and to reduce the vibrations transmitted to the handle as a result of torsional vibrations.
  • the object is achieved in that the first spring-loaded bearing along the second direction has a substantially lower spring stiffness than in the first direction.
  • the decoupling of the handle from the vibrations generated by the torsional vibrations about the center of gravity on the housing takes place along the second direction substantially by the spring action on the second spring-loaded bearing.
  • a disadvantageous influence on the decoupling of torsional vibrations by a spring action of the first spring-loaded bearing is largely avoided. This makes it possible to achieve a particularly effective decoupling of the handle from the torsional vibrations, which in turn allows a particularly comfortable handling of the power tool during operation.
  • the first spring-loaded bearing has a first housing-side bearing device fixedly connected to the housing and a first grip-side bearing device fixedly connected to the handle. Between these two first bearing devices, a first spring device is provided, by means of which these are resiliently supportable from one another, specifically in the first direction. In contrast, in the second direction between the first storage facilities a permanent free space is provided to minimize a spring action in this direction. In this way, the handle can be particularly well decoupled from the torsional vibrations occurring in operation on the housing and the resulting vibrations along the second direction, wherein the high feed forces to be absorbed in the first direction can be absorbed by a high spring stiffness.
  • one of the first bearing means comprises a first latch-shaped bearing member extending parallel to a third direction perpendicular to the first direction and the second direction.
  • the other first bearing device has a first tubular bearing element radially enclosing the first tubular bearing element.
  • the first bearing device is supported with the first latch-shaped bearing element in the first direction to a first side with the interposition of the first spring means permanently on the first tubular bearing element.
  • the first bearing device with the first latch-shaped bearing element depending on a pressure applied to the handle contact pressure, can be applied to the first tubular bearing element or spaced from this.
  • a good vibration isolation in the first direction can be achieved in a required for example for the operation of the hammer mechanism, applied to the handle contact pressure.
  • a negative contact pressure that is, when applying a tensile force on the handle a particularly direct penetration of the handle on the rest of the device ensures, for example, when jammed tool to apply the most direct force on this can to solve it again.
  • the first spring means comprises a first elastomeric device having on the first side of the first latch-shaped bearing element a biasing region which has a multiple greater extension with respect to the first direction than a stopper area on the second side of the latch-shaped bearing element and in the second direction both sides of the first latch-shaped bearing element has a permanent distance from the first tubular bearing element.
  • the Elastomer device can be made for example of a foamed plastic, such as polyurethane in particular. In this way, a particularly favorable spring action on the biasing region can be achieved, which ensures a good decoupling and thereby a significantly reduced vibration transmission to the handle.
  • the biasing region made of foamed elastomer a higher spring stiffness can be ensured with increasing contact pressure, which enables good guidance of the hand tool device even under heavy load.
  • the permanent distance of the elastomeric device which is maintained with regard to the second direction on both sides relative to the first tubular bearing element, ensures that no essential spring action occurs in this second direction. Only by the biasing region extending along the first direction is a certain spring action along the second direction generated over the cross section thereof, which, however, is significantly smaller than the spring rigidity in the first direction.
  • the first elastomeric device has a first support region which has a smaller extension along the first direction than the biasing region.
  • a targeted progression of the spring stiffness of the first spring device can be achieved above a certain relative movement of the handle relative to the housing.
  • a defective contact between the handle and the housing can be prevented, for example, even at very high contact pressures.
  • the second spring-loaded bearing in the second direction a higher spring stiffness than the first spring-loaded bearing, that is.
  • the second spring-loaded bearing advantageously has a second latch-shaped bearing element, which is radially enclosed by a second tubular bearing element with the interposition of a second elastomeric device, the second elastomeric body having a region with a star-shaped cross section.
  • a second elastomeric device allows a particularly good setting of a predetermined spring stiffness, which acts evenly in the radial direction about the second locking element around the bar.
  • a relatively soft spring action in the direction of rotation can be generated around the second latch-shaped bearing element. All in all This results in a particularly good decoupling of the handle against the vibrations generated due to torsional vibration achieved on the housing.
  • the second elastomeric device between the second latch-shaped bearing element and the second tubular bearing element has a second support region which has a smaller radial extent circumferentially than the region with a star-shaped cross-section.
  • a targeted progression of the spring stiffness of the second elastomer device can be achieved at the second spring-loaded bearing from a certain relative movement of the handle relative to the housing in the radial direction of the second latch-shaped bearing element.
  • the additional increase of the spring characteristic by the second support region can be adjusted by its special training, such as by a certain cross-sectional shape, a variable density or specific length. In any case, this can be prevented at very high contact pressures or when releasing a jammed tool on the second spring-loaded bearing a defective contact between the handle and the housing.
  • Fig. 1 shows the basic structure of a hand tool 2 in the form of an optionally used as a drill or chisel hammer electro combi hammer.
  • This has a housing 4, in which a drive motor 6 and driven by this electro-pneumatic impact mechanism 8 are housed.
  • the impact mechanism 8 has a working means 10 in the form of a percussion piston, which is reciprocated during operation along a working axis A, by which a parallel first direction z is fixed.
  • the working axis A in this case has a distance from a center of gravity S of the hand tool 2, which may be defined, for example, by the center of mass of the hand tool 2 in the middle position of the working means 10.
  • a handle 14 is held, which extends substantially along a second direction y, which is perpendicular to the first direction z.
  • This is connected to the housing 4 via a total of 16 designated Entkoppelungsan eleven.
  • the decoupling arrangement 16 has a first spring-loaded bearing 18, which is arranged adjacent to the working axis A, and a second spring-loaded bearing 20 in the form of a rotary bearing, which is arranged at a distance from the working axis A and the first spring-loaded bearing 18 with respect to the second direction y ,
  • the first spring-loaded bearing 18 has a first housing-side bearing device 22 with a first latch-shaped bearing element 24 which is enclosed by a first tubular bearing element 26 of a first grip-side bearing device 28.
  • a first tubular bearing element 26 of a first grip-side bearing device 28 any other circumferential training can be selected.
  • first latch-shaped bearing element 24 is supported along the first direction z toward a first side 30 via a first spring device 32, which is schematically represented here by a helical spring but can also be formed by other suitable spring means on the first tubular bearing element 26 , Towards a second side 34, which lies opposite the first side 30, the latch-shaped bearing element 24 rests against the tubular bearing element 26 via a stop 37 formed by a shaped part 36, in the unloaded state of the handheld power tool 2 shown here.
  • first spring device 32 which is schematically represented here by a helical spring but can also be formed by other suitable spring means on the first tubular bearing element 26 .
  • the second spring-loaded bearing 20 has a second housing-side bearing device 38 with a second latch-shaped bearing element 40 which is enclosed by a second tubular bearing element 42 of a second grip-side bearing device 44.
  • the second latch-shaped bearing element 24 is supported in the radial direction circumferentially via a second spring device 46, which is shown schematically here by four coil springs but may also be formed by other suitable spring means, on the second tubular bearing element 42 from.
  • Fig. 2 shows the hand tool 2 in operation.
  • the handle 14 is acted upon by a contact pressure P1, P2, through which the hand tool 2 is pressed by a tool T against a material to be machined M.
  • the handle 14 is in this case together with the two tubular bearing elements 26, 42 against a respective spring force F of the two spring means 32, 46 in the first direction z on the housing 4 moves.
  • the abutment 37 of the molded part 36 held on the first latch-shaped bearing element 24 is spaced from the first tubular bearing element 26.
  • the first latch-shaped bearing element 24 in the first direction z can oscillate freely with respect to the first tubular bearing element 26 under spring action of the first spring device 32.
  • the latch-shaped bearing element 24, or the molded part 36 held thereon always has a distance in relation to the first tubular bearing element 26 on both sides for all forces acting in the intended operation.
  • the spring action of the first spring device 32 in the second direction y is reduced to a minimum.
  • the first spring-loaded bearing 18 has a lower spring stiffness along the second direction y than along the first direction z.
  • the second latch-shaped bearing element 40 is still supported by the second spring device 46 to all sides radially relative to the second tubular bearing element 42.
  • the spring constant or the spring constant of the second spring-loaded bearing 20 is higher than the spring constant of the first spring-loaded bearing 18.
  • the construction as a pivot bearing also ensures a spring action in the direction of rotation D about the second latch-shaped bearing element 40 around.
  • the second latch-shaped bearing element 40 in the first direction z, in the second direction y and also in the direction of rotation D freely under spring action of the second spring means 46 swing freely relative to the second tubular bearing element 42, wherein in the second direction y a disturbing interference by the Spring action of the first spring-loaded bearing 18 is omitted.
  • the handle 14 can also be decoupled in all directions against torsional vibrations indicated by the arrow DS that arise on the housing 4 due to the distance of the center of gravity S from the working axis A.
  • the first spring device 32 is essentially formed by an elastomer device made of foamed polyurethane.
  • the spring device 32 is formed in several parts and has two substantially anvil-shaped elastomeric body 48 and two provided therebetween collar-shaped elastomer body 50, all of which are pushed onto the aligned parallel to a third direction x first locking element bearing 24, wherein the third direction x both against the the first direction z and with respect to the second direction y is perpendicular.
  • the anvil-shaped elastomeric bodies 48 have in the first direction z on the first side 30 of the first latch-shaped bearing element 24 a biasing region 52 which extends further in the first direction z than a likewise respectively provided on the first side 30 support region 54 of the two collar-shaped Elastomer body 50.
  • the two anvil-shaped elastomer body 48 each form a tapered stop region 49.
  • This abutment region 49 has, in the first direction z, an extension which is only a fraction of the extent of the pretensioning region 52 in the first direction.
  • two end-side elastomeric bodies 56 are provided, which are arranged in the installed state in each case between a side part 58 of the first housing-side bearing device 22 and a front-side flange 60 of the first tubular bearing element 26.
  • a vibration reduction is also achieved in operation in the third direction x by at least partial decoupling of the first grip-side bearing device 28 from the first housing-side bearing device 22.
  • the first spring-loaded bearing 18 by two fasteners 62, can be completely pre-assembled. These project through a respective receiving bore 64 of the side parts 58 and are fixed in a longitudinal bore 66 of the first latch-shaped bearing element 24, which are shown in FIG. 3.
  • FIG. 5 shows the first spring-loaded bearing 18 in an unloaded starting position according to FIG. 1.
  • the tapered stop 37 rests against a receiving groove 68 of the first tubular bearing element 26.
  • the biasing region 52 is supported opposite to a bearing groove 70 of the first tubular bearing element 26.
  • a certain fixation of the first latch-shaped bearing element 24 relative to the first tubular bearing element 26 is achieved in the unactuated state of the power tool 4 in the second direction y.
  • the anvil-shaped elastomer body 48 together with the first tubular bearing element 26 in the second direction y, forms an intermediate space 47 on both sides.
  • the stop 37 is removed from the receiving groove 68 in the first direction z.
  • the gaps 47 remain, albeit recurring with reduced volume, permanently maintained during operation.
  • a small spring effect can thus be generated only via the biasing region 52 pressed against the bearing groove 70.
  • the biasing region 52 can also be compressed to such an extent that the first tubular bearing element 26 comes into contact with the support region 54 of the collar-shaped elastomer body 50 in the first direction z. In this case, we specifically increases the spring rigidity of the first spring device 32 in the first direction z.
  • the second spring device 46 is essentially formed by an elastomer device made of foamed polyurethane.
  • the second spring means 46 is formed in several parts and has two substantially star-shaped elastomer body 72 and two provided therebetween annular elastomer body 74, all of which are pushed onto the parallel to the third direction x aligned second latch-shaped bearing member 40.
  • the star-shaped elastomer bodies 72 extend in the radial direction around the second latch-shaped bearing element 40 further than the two annular elastomer bodies 74.
  • two end-face elastomeric bodies 76 are also provided here, which are each arranged in the installed state between a side part 78 of the second housing-side bearing means 38 and an end flange 80 of the second tubular bearing element 42.
  • a vibration reduction is also achieved in operation in the third direction x by at least partial decoupling of the second grip-side bearing device 44 from the second housing-side bearing device 38.
  • the second spring-loaded bearing 20 by two fasteners 82 can be completely pre-assembled. These project through a respective receiving bore 84 of the side parts 78 and are each fixed in a longitudinal bore 86 of the second latch-shaped bearing element 40, which are shown in FIG. 6.
  • FIG. 8 shows the second spring-loaded bearing 20 in an unloaded starting position according to FIG. 1.
  • the star-shaped elastomer bodies 72 have approximately the same spring stiffness in all radial directions around the second locking element 40, which is greater than the spring stiffness. which has the first spring-loaded bearing 18 with respect to the first tubular bearing element 26 spaced stop 37 in the second direction y.
  • the star-shaped elastomer body 72 can also be compressed to the extent that the second tubular bearing element 42 comes into abutment in the relevant direction with the annular elastomer bodies 74, which act as a second support area. In this case, we selectively increases the spring stiffness of the second spring means 46 in this direction progressively.
  • the second spring-loaded bearing 20 also in the direction of rotation D has a certain spring action, which decouples the handle 14 with respect to a rotational movement of the housing 4.
  • each of the spring devices 32, 46 configured as an elastomer device
  • a plurality of the elastomeric bodies 48, 50, 56; 72, 74, 76 also be formed in one piece.
  • the second spring means 46 may alternatively be formed in addition to the illustrated embodiment by a leaf spring, but would have to allow the same degrees of freedom in all three directions x, y, z.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP07112663.5A 2006-07-27 2007-07-18 Outil à main doté d'un dispositif de découplage Active EP1882559B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006000375A DE102006000375A1 (de) 2006-07-27 2006-07-27 Handwerkzeuggerät mit Entkoppelungsanordnung

Publications (2)

Publication Number Publication Date
EP1882559A1 true EP1882559A1 (fr) 2008-01-30
EP1882559B1 EP1882559B1 (fr) 2014-06-04

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Family Applications (1)

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EP07112663.5A Active EP1882559B1 (fr) 2006-07-27 2007-07-18 Outil à main doté d'un dispositif de découplage

Country Status (4)

Country Link
US (1) US7610967B2 (fr)
EP (1) EP1882559B1 (fr)
JP (1) JP5124195B2 (fr)
DE (1) DE102006000375A1 (fr)

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EP2082845A2 (fr) 2008-01-24 2009-07-29 Black & Decker, Inc. Ensemble de montage pour poignée d'outil électrique
EP2103392A1 (fr) * 2008-03-18 2009-09-23 Black & Decker, Inc. Marteau
EP3626399A1 (fr) 2018-09-20 2020-03-25 Hilti Aktiengesellschaft Machine-outil portative et procédé de fonctionnement d'une machine-outil portative
EP3943251A1 (fr) * 2020-07-22 2022-01-26 Hilti Aktiengesellschaft Dispositif d'amortissement des chocs pour un accumulateur

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DE102007055843A1 (de) * 2007-12-17 2009-06-25 Hilti Aktiengesellschaft Handwerkzeugmaschine mit Schwingungsausgleicher
GB0804963D0 (en) * 2008-03-18 2008-04-16 Black & Decker Inc Hammer
US7938196B2 (en) * 2009-04-17 2011-05-10 Hilti Aktiengesellschaft Hand-held power tool with vibration-compensating mass
DE102009002589A1 (de) * 2009-04-23 2010-10-28 Hilti Aktiengesellschaft Handwerkzeugmaschine
JP5436071B2 (ja) * 2009-07-02 2014-03-05 株式会社マキタ 作業工具
JP5502458B2 (ja) 2009-12-25 2014-05-28 株式会社マキタ 打撃工具
JP5496812B2 (ja) * 2010-08-03 2014-05-21 株式会社マキタ 作業工具
US20120048580A1 (en) * 2010-09-01 2012-03-01 Hilti Aktiengesellschaft Power tool
DE102010040173A1 (de) * 2010-09-02 2012-03-08 Hilti Aktiengesellschaft Handwerkzeugmaschine
US8966773B2 (en) 2012-07-06 2015-03-03 Techtronic Power Tools Technology Limited Power tool including an anti-vibration handle
KR101389960B1 (ko) * 2012-09-12 2014-04-29 한양대학교 에리카산학협력단 전동공구용 진동저감장치
JP6096593B2 (ja) * 2013-05-29 2017-03-15 株式会社マキタ 往復動式作業工具
EP2898991B1 (fr) * 2014-01-23 2018-12-26 Black & Decker Inc. Poignée arrière
EP2898994A1 (fr) 2014-01-23 2015-07-29 Black & Decker Inc. Outil électrique avec une poignée arrière
EP2898993B1 (fr) 2014-01-23 2019-01-30 Black & Decker Inc. Outil electrique
EP2898992B1 (fr) * 2014-01-23 2016-05-04 Black & Decker Inc. Outil électrique avec poignée arrière, méthode d'assemblage d'une partie d'une poignée pour un outil électrique et méthode de démontage d'une partie d'une poignée pour un outil électrique
JP6620434B2 (ja) * 2015-06-12 2019-12-18 マックス株式会社 打撃工具
EP3501750A1 (fr) * 2017-12-19 2019-06-26 Hilti Aktiengesellschaft Machine-outil portative à vibrations amorties
CN110549303A (zh) * 2018-05-31 2019-12-10 苏州宝时得电动工具有限公司 冲击工具
CN108747937B (zh) * 2018-06-12 2020-02-28 国网山东省电力公司烟台供电公司 一种绝缘电动扳手
US12021437B2 (en) 2019-06-12 2024-06-25 Milwaukee Electric Tool Corporation Rotary power tool
JP2022119301A (ja) * 2021-02-04 2022-08-17 株式会社マキタ 打撃工具
JP2022128006A (ja) * 2021-02-22 2022-09-01 株式会社マキタ 打撃工具
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Cited By (9)

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EP2082845A2 (fr) 2008-01-24 2009-07-29 Black & Decker, Inc. Ensemble de montage pour poignée d'outil électrique
EP2082845A3 (fr) * 2008-01-24 2011-09-14 Black & Decker, Inc. Ensemble de montage pour poignée d'outil électrique
US8708059B2 (en) 2008-01-24 2014-04-29 Black & Decker Inc. Mounting assembly for handle for power tool
EP2103392A1 (fr) * 2008-03-18 2009-09-23 Black & Decker, Inc. Marteau
US7886838B2 (en) 2008-03-18 2011-02-15 Black & Decker Inc. Hammer
EP3626399A1 (fr) 2018-09-20 2020-03-25 Hilti Aktiengesellschaft Machine-outil portative et procédé de fonctionnement d'une machine-outil portative
WO2020058031A1 (fr) 2018-09-20 2020-03-26 Hilti Aktiengesellschaft Machine-outil portative et procédé pour faire fonctionner une machine-outil portative
EP3943251A1 (fr) * 2020-07-22 2022-01-26 Hilti Aktiengesellschaft Dispositif d'amortissement des chocs pour un accumulateur
WO2022017846A1 (fr) * 2020-07-22 2022-01-27 Hilti Aktiengesellschaft Dispositif d'amortissement des chocs pour accumulateur

Also Published As

Publication number Publication date
EP1882559B1 (fr) 2014-06-04
US7610967B2 (en) 2009-11-03
DE102006000375A1 (de) 2008-01-31
US20080047724A1 (en) 2008-02-28
JP2008030192A (ja) 2008-02-14
JP5124195B2 (ja) 2013-01-23

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